EP0348861A2 - Hydraulisch zu betätigende Kettenspanneinrichtung - Google Patents

Hydraulisch zu betätigende Kettenspanneinrichtung Download PDF

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Publication number
EP0348861A2
EP0348861A2 EP89111595A EP89111595A EP0348861A2 EP 0348861 A2 EP0348861 A2 EP 0348861A2 EP 89111595 A EP89111595 A EP 89111595A EP 89111595 A EP89111595 A EP 89111595A EP 0348861 A2 EP0348861 A2 EP 0348861A2
Authority
EP
European Patent Office
Prior art keywords
chamber
plunger
body member
bore
fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP89111595A
Other languages
English (en)
French (fr)
Other versions
EP0348861A3 (en
EP0348861B1 (de
Inventor
Mark Stewart Breon
Bryce Allen Buuck
Leslie Lee Ecklund
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Eaton Corp
Original Assignee
Eaton Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Eaton Corp filed Critical Eaton Corp
Publication of EP0348861A2 publication Critical patent/EP0348861A2/de
Publication of EP0348861A3 publication Critical patent/EP0348861A3/en
Application granted granted Critical
Publication of EP0348861B1 publication Critical patent/EP0348861B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/0848—Means for varying tension of belts, ropes, or chains with means for impeding reverse motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0806—Compression coil springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0812—Fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/0848—Means for varying tension of belts, ropes, or chains with means for impeding reverse motion
    • F16H2007/0859—Check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0889—Path of movement of the finally actuated member
    • F16H2007/0891—Linear path

Definitions

  • This invention relates generally to a pressurized fluid operated device for tensioning an endless roller chain or belt and more particularly to such device including at least one air vent oriented so as to enable the device to be transversely rotated a predetermined angular amount relative a horizontal plane whilst remaining operative to enable entrapped air to escape from the pressurized fluid and preventing the fluid when not pressurized to drain from the device under gravity in any substantial amount.
  • a great many hydraulic devices have been developed over the years for tensioning endless roller chains and belts particularly in vehicular applications.
  • Some prior art devices feature a pressurized fluid operated piston whose exposed end has been adapted to engage the chain or belt without unduly inhibiting its movement and is operative to displace the chain or belt transversely to tension it as the piston rod is caused to move towards the chain or belt in response to pressurized fluid being conveyed into the piston chamber.
  • Other prior art devices include resilient biasing means such as a coiled spring in the piston chamber to either urge the piston rod towards the chain or belt in conjunction with the pressurized fluid or in some cases to urge the piston rod in an opposite direction to lessen the force of the pressurized fluid on the piston rod so that the roller chain or belt is not over tensioned.
  • the fluid selected is an incompressible fluid such as oil which acts as an incompressible medium within the fluid reservoir.
  • the fluid pressure in the high pressure chamber will subsequently decrease due to the enlargement of the high pressure chamber arising by movement of the piston towards the rod or cam and/or due to leakage until it falls below the fluid pressure in the reservoir which again causes the check valve to open and enable the fluid to pass from the reservoir into the high pressure chamber to provide cyclic recharging of fluid in the high pressure chamber.
  • the chain or belt tensioning device of the present invention not only enables entrapped air to be vented when it is being filled with the fluid and during its operation but also enables a broad orientation range of the device relative a horizontal plane without an appreciable amount of the fluid draining therefrom under gravity when not pressurized.
  • FIGURE 1 shows a vehicular engine application for which the tensioning device of the invention can be used to great advantage.
  • FIGURE 1 shows an engine crank shaft 6 driving a pair of spaced-apart cam shafts 4 by means of belt or roller chains 2 and 3. Since crank shaft (6) and cam shafts (4) are normally fixed in their locations, it is likely that, although originally suitably tensioned, roller chains or belts 2 and 3 will loosen after a period of time due to stretching and wear of either the chain or belt and/or the sheaves or sprockets employed with the belt or roller chain.
  • two tensioning devices 300 are employed in two different orientations relative a horizontal plane that are respectively operatively engaged with a pivotable paddle 8 and are effective to pivot paddle 8 and move chains or belts 2 and 3 in a direction and for a distance sufficient to maintain a suitable tension thereon.
  • the device of the invention will automatically take up slack in belts or roller chains 2 and 3 due to stretch and wear and is further operative to be transversely rotated a predetermined angular amount relative a horizontal plane whilst enabling entrapped air to escape from a pressurized fluid reservoir therewithin without enabling a substantial amount of fluid to drain from the device by gravity when not pressurized to vastly increase its versatility and usefulness in a variety of applications.
  • Fluid operated devices made in accordance with the invention commonly are able to vent air that may be entrapped in their respective fluid reservoir chambers through the clearance between the bore wall and the outer periphery of their respective dynamic plungers or pistons when the piston is within a prescribed position range relative vertical but which further include at least one vent extending through the body of the device that preferably angularly intersects the fluid chamber and enables entrapped air to be vented from the chamber when the device is rotated a predetermined angular amount relative a horizontal plane as hereafter described.
  • device 300 perhaps illustrates the invention in one of its simplest forms.
  • Device 300 has a body member 10 having a pair of spaced-apart openings or holes 28 therethrough for bolting it to a frame.
  • holes 28 through body member 10 are preferred for mounting, any suitable means may be employed for mounting the body member of the tensioning device of the invention to a frame such as a cylinder head or engine block.
  • Body member 10 has a bore 12 therein having an open end 17 and a closed end 14.
  • a dynamic plunger 16 is slidably received in bore 12.
  • Plunger 16 has an exposed end 18 and an opposite end 20 within bore 12 and spaced-apart from closed end 14 to define a first fluid pressure chamber or reservoir 24 within bore 12 therebetween.
  • Means such as passageway 13 is provided in body member 10 for conveying pressurized fluid from a pressurizing source such as a pump into chamber 24 as shown in FIGURE 2. In vehicular applications the fluid pressure is commonly in the range of 10 to 70 psig.
  • Exposed end 18 of plunger 16 is operatively engaged with the chain or belt, in this case, by means of pedestal 22 secured thereto which is shaped to engage paddle 8 as hereinbefore described with respect to FIGURE 1.
  • the extended position of pedestal 22 is shown in dashed line form and generally is a function of the stroke of plunger 16 which in turn is a function of the length of both bore 12 and plunger 16.
  • Device 300 preferably includes a resilient biasing means such as coiled spring 26 in chamber 24 that operates to urge plunger 16 away from closed end 14 of bore 12 to assist the fluid pressure in tensioning the chain or belt.
  • a resilient biasing means such as coiled spring 26 in chamber 24 that operates to urge plunger 16 away from closed end 14 of bore 12 to assist the fluid pressure in tensioning the chain or belt.
  • chamber 24 Once chamber 24 is filled with pressurized fluid such as oil, it acts as an incompressible fluid against which paddle 8 acts to maintain tension on the chain or belt.
  • pressurized fluid such as oil
  • Body member 10 includes a pair of spaced-apart air vents 30 and 32 that respectively angularly intersect opposite ends of chamber 24 and are oriented relative bore 12 in such a manner that device 300 can be rotated transversely a predetermined angular amount relative a horizontal plane such as shown in FIGURE 1, with at least one of vents 30 and 32 operable to enable entrapped air to escape from chamber 24 whilst neither enables a substantial amount of the fluid, when not pressurized, to drain from chamber 24.
  • vent 32 is operable to vent entrapped air from chamber 24 and the slope of both vents 30 and 32 relative horizontal is greater than zero allowing air to travel upwardly and out from chamber 24 while preventing the fluid from draining from chamber 24 by gravity when not pressurized.
  • pressurized fluid is vented by both vents 30 and 32 and entrapped air is vented by at least one of vents 30 and 32 and neither operate to enable unpressurized fluid to drain from chamber 24 by gravity whilst device 300 is within a predetermined orientation range relative a horizontal plane.
  • tensioning device 400 has a body member 36 provided with an open ended bore 38 in which dynamic plunger 44 is slidingly received.
  • the operation of device 400 is essentially the same or for device 300 hereinbefore described.
  • Plunger 44 is spaced-apart from the closed end of bore 38 to provide a first fluid chamber or reservoir 40 therebetween. Pressurized fluid enters chamber 40 through opening 50.
  • An annular space 42 is provided between the outer periphery of plunger 44 and the inner surface of body member 36 surrounding bore 38. Space 42 is in fluid communication with chamber 40 and forms a part thereof.
  • Vent 48 intersects chamber 40 adjacent the closed end of bore 38 such that device 400 can be transversely rotated a predetermined angular amount relative a horizontal plane with vent 48 maintaining a slope B greater than zero and remaining operable to vent entrapped air from chamber 40 and to prevent a substantial amount of the fluid to drain from chamber by gravity when unpressurized.
  • Vent 48 preferably includes a flow restrictor 51 for minimizing the flow of pressurized fluid through vent 48 when device 400 is operating with pressurized fluid in chamber 40.
  • FIGURES 4A and 4B A preferred embodiment of the invention in the form of tensioning device 500 is shown in FIGURES 4A and 4B.
  • device 400 has been rotated clockwise by angle alpha relative horizontal plane "P" from the position shown in FIGURE 4A.
  • Device 500 has a body member 52 having a close-ended bore 54 therein in which dynamic plunger 56 is slidably received.
  • Plunger 56 has a close-ended bore (not referenced) in the end thereof facing towards the closed end of body member bore 54.
  • the end of plunger 56 is spaced-apart from the closed end of bore 54 to define a first fluid chamber 60 therebetween.
  • a static plunger 58 having a hollow interior 64 is stationarily disposed within chamber 60 with a portion thereof extending into the dynamic plunger 56 bore and spaced-apart from the bottom thereof to define a second fluid chamber or reservoir 72 therebetween.
  • An opening 62 through the wall of static plunger 58 provides fluid communication between chamber 60 and hollow interior 62.
  • An opening 68 in the wall of static plunger 58 provides fluid communication between chamber 72 and hollow interior 64.
  • a resilient check valve 70 is provided that operates to enable pressurized fluid to flow from hollow interior 64 into chamber 72 when dynamic plunger 56 is moving away from stator plunger 58 which creates a vacuum in chamber 72 resulting in check valve 10 opening to allow fluid to flow from hollow interior or reservoir 64 into chamber 72.
  • Static plunger 58 is provided with an integral flange or a washer 59 supported by a snap-ring, that extends radially outwardly from its outer periphery providing a surface upon which to rest an end of a resilient biasing means such as coiled spring 66 whose opposite end engages an end of plunger 56 within bore 54.
  • Spring 66 operates to both urge plunger 58 away from the closed end of bore 12 and to urge static plunger 58 thereagainst to provide the stationary relationship therefore relative bore 12.
  • Other means may be used to secure static plunger 58 stationarily within bore 12.
  • a space 75 is provided between the outer periphery of dynamic plunger 56 and the surface of body member 52 surrounding bore 12. Space 75 is in fluid communication with chamber 60 and forms a part thereof.
  • a means is provided for conveying pressurized fluid into chamber 60 which in turn then flows through opening 62 into hollow interior 64 which acts as a reservoir for chamber 72 into which the pressurized fluid flows when its pressure exceeds that in chamber 72 by a predetermined amount.
  • Device 500 includes an air vent 76 that angularly intersects chamber 60 adjacent the closed end of bore 54.
  • Vent 76 is respectively oriented relative bore 12 such that device 400 can be transversely rotated an angle alpha relative horizontal plane "P", as shown in FIGURE 4B whilst maintaining a slope B greater than zero and remaining operable to vent entrapped air from chamber 60 and preventing a substantial amount of fluid to drain under gravity from either chamber 60 or hollow interior 64 when unpressurized.
  • Device 600 of FIGURES 5A and 5B has a body member 78 having a close-ended bore 80 therein in which a dynamic plunger 82 is slidably received.
  • the end of plunger 82 within bore 80 is spaced-apart from the closed end thereof to define a first fluid chamber or reservoir 90 therebetween.
  • a static plunger 84 having a hollow interior 86 is stationarily secured within chamber 90 and a means is provided (not shown) for conveying pressurized fluid into chamber 90 which in turn flows into hollow interior 86 through a depression such as a slot or groove 88 in the closed end of bore 80.
  • a resilient coiled spring 83 is disposed within chamber 90 which operates to urge dynamic plunger 82 away from the closed end of bore 80 as well as urge static plunger 84 against the closed end of bore 80 to provide the stationary relationship therefor.
  • a portion of static plunger 84 extends into a close-ended bore, not referenced, in dynamic plunger 82 and is spaced-apart therefrom to define a second high pressure fluid chamber 94 therebetween.
  • An opening 92 is provided between chamber 94 and hollow interior 86, and a check valve 96 is included which controls pressurized fluid flow between hollow interior 86 and chamber 94 as previously described for device 500.
  • a first air vent 98 angularly intersects chamber 90 adjacent the closed end of bore 80 and a second air vent 100 extends through dynamic plunger 80 between chamber 90 and the exposed end of plunger 80.
  • Vent 100 is operable to convey both entrapped air and pressurized fluid to the exposed end of plunger 100 which may, for example, be used to lubricate a roller chain being tensioned by device 600.
  • Vent 98 is oriented relative bore 80 to enable device 600 to be rotated a predetermined angular amount alpha relative a horizontal plane "P" with vent 98 maintaining a slope B greater than zero and remaining operable to enable entrapped air to escape from chamber 90 and preventing a substantial amount of fluid to drain by gravity from either chamber 90 or hollow interior 86 when the fluid is not in a pressurized state.
  • Device 700 of FIGURE 6 has a body member 102 having a close-ended bore 104 in which dynamic plunger 106 is slidably received.
  • the end of plunger 106 is spaced-apart from the closed end of bore 104 to define a first fluid chamber 111 therebetween.
  • a static plunger 108 having a hollow interior or fluid reservoir 112 is stationarily disposed within chamber 111 by means of coiled spring 109 which operates to urge static plunger 108 and dynamic plunger 106 away from each other as previously described.
  • a depression such as a slot or groove 110 in the closed end of bore 104 enables pressurized fluid to flow between chamber 111 and hollow interior 112 from a pressurized fluid source (not shown).
  • a portion of static plunger 108 extends into a close-ended bore (not referenced) in plunger 106 facing towards chamber 111 and is spaced-apart from the closed end thereof to define a second high pressure fluid chamber 107 therebetween.
  • An opening 114 and check valve means 116 enable pressurized fluid to flow from hollow interior 112 into chamber 107 as hereinbefore described.
  • Device 700 has an air vent 120 that angularly intersects chamber 111 adjacent the closed end of bore 124 and exits at the right side of body member 102.
  • Vent 120 is plugged at its exit from body member 102 by suitable means such as plug 119 as shown in FIGURE 6.
  • a second vent or branch 121 of vent 120 extends from an exit at the bottom of body member 102 in substantial parallel alignment with the axis of bore 104 and intersects vent 120 as shown in FIGURE 6 to provide a "knee" between vents 120 and 121.
  • a fluid flow restrictor 123 is preferably included at the exit of vent 121 at the bottom of body member 102.
  • plug 119 may be removed from vent 120 and flow restrictor 123 replaced with a plug such that device 700 is operable to be rotated a predetermined angular amount relative horizontal with the slope of vent 120 remaining greater than zero enabling vent 120 to vent entrapped air from chambers 111 and 112 yet operable to prevent a substantial amount to drain therefrom under gravity when unpressurized.
  • FIGURE 6 where vent 120 is plugged and vent 121 is not, can be used to particular advantage in tensioning short cam to cam chain drives in dual overhead cam engines where device 700 is positioned within the loop of the chain.
  • device 700 can be rotated toward the viewer's left such that the included angle between the axis of bore 104 and horizontal is about 45 degrees for tensioning the chain drive between the left bank of cams when viewed from the front of the engine and also can be rotated 180 degrees about the axis of bore 104 and then rotated towards the viewer's right such that the included angle between the axis of bore 104 and horizontal is about 45 degrees for tensioning the short chain between the right bank of cams of the dual overhead cam engine.
  • vent 120 In both the left or right position, the slope of vent 120 relative horizontal is greater than zero enabling entrapped air to vent through vent 121 from chamber 111 and 112 and yet prevent a substantial amount of fluid to drain therefrom under gravity when not pressurized whilst enabling pressurized fluid to flow from the exit of vent 121 at the bottom of device 700 for lubricating the chain as it passes the bottom of device 700.
  • Device 800 of FIGURE 7 is similar to device 600 previously described except that it has a dynamic plunger 126 having a composite wall construction featuring an inner portion 139 separated from an outer section 124 by a space 142 which is operative to receive pressurized fluid from opening 128 and convey it to a vent 144 in portion 126 which then conveys it to the exposed end of plunger 126, for example, for lubrication purposes.
  • Such composite construction eliminates the complexities of drilling or casting the air vent in the dynamic plunger and is effective to provide greater flow rate of the pressurized fluid through the dynamic plunger.
  • An air vent 146 angularly intersects a first fluid chamber 130 adjacent the closed end of bore 144 in body member 140.
  • a depression such as a slot or groove 143 in the closed end of bore 144 enables pressurized fluid to flow from chamber 130 into hollow interior or reservoir 141 of static plunger 148.
  • Vent 146 is oriented relative bore 144 to enable device 800 to be transversely rotated a predetermined angular amount relative horizontal whilst maintaining a slope greater than zero and remaining operable to enable entrapped air to escape from chambers 130 and 141 yet prevent a substantial amount of fluid to drain under gravity therefrom when unpressurized.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
EP89111595A 1988-07-01 1989-06-26 Hydraulisch zu betätigende Kettenspanneinrichtung Expired - Lifetime EP0348861B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US07/217,901 US4826470A (en) 1988-07-01 1988-07-01 Fluid operated chain or belt tensioning device
US217901 1988-07-01

Publications (3)

Publication Number Publication Date
EP0348861A2 true EP0348861A2 (de) 1990-01-03
EP0348861A3 EP0348861A3 (en) 1990-06-13
EP0348861B1 EP0348861B1 (de) 1993-11-03

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP89111595A Expired - Lifetime EP0348861B1 (de) 1988-07-01 1989-06-26 Hydraulisch zu betätigende Kettenspanneinrichtung

Country Status (4)

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US (1) US4826470A (de)
EP (1) EP0348861B1 (de)
JP (1) JPH0257750A (de)
DE (1) DE68910396T2 (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0621419A1 (de) * 1993-04-20 1994-10-26 JOH. WINKLHOFER & SÖHNE GmbH & Co KG Kettenspanner mit Federvorspannung und hydraulischer Dämpfung
EP0472505B1 (de) * 1990-08-20 1995-09-27 TECNIDEA CIDUE S.r.l. Spannvorrichtung
EP0686787A1 (de) * 1994-06-06 1995-12-13 JOH. WINKLHOFER & SÖHNE GmbH & Co KG Hydraulische Spanneinrichtung für endlose, flexible Getriebeelemente
GB2345112A (en) * 1998-12-22 2000-06-28 Sachs Automotive France Sa Hydraulic chain tensioner having a gas-purging orifice
EP1498580A2 (de) * 2003-07-16 2005-01-19 Renold Plc Ketten- oder Riemenspanner
US7634949B2 (en) 2005-07-23 2009-12-22 Renold Plc Transmission chain monitoring system

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JP2775736B2 (ja) * 1987-09-30 1998-07-16 アイシン精機株式会社 オートテンシヨナー
US4976661A (en) * 1989-08-21 1990-12-11 Nhk Spring Co., Ltd. Belt or chain tensioner for power transmitting system
DE4023728A1 (de) * 1990-07-26 1992-01-30 Porsche Ag Kettenspanner fuer eine brennkraftmaschine
US5259820A (en) * 1992-05-19 1993-11-09 Borg-Warner Automotive Transmission & Engine Components Corporation Hydraulic tensioner having a variable orifice check valve and a double helix internal ratchet
US5370584A (en) * 1993-01-15 1994-12-06 Borg-Warner Automotive, Inc. Piston design for removing air from a hydraulic tensioner
US5346436A (en) * 1993-09-23 1994-09-13 Borg-Warner Automotive, Inc. Air vent for hydraulic chain tensioner
US5601505A (en) * 1994-09-12 1997-02-11 Borg-Warner Automotive, K.K. Hydraulic tensioner
JP2854261B2 (ja) * 1995-04-28 1999-02-03 株式会社椿本チエイン 油圧式テンショナ
US5643117A (en) * 1995-12-08 1997-07-01 Borg-Warner Automotive, Inc. Hydraulic tensioner with check valve vent
JP3722909B2 (ja) * 1996-05-10 2005-11-30 ボルグワーナー・モールステック・ジャパン株式会社 油圧テンショナ
JP3752017B2 (ja) * 1996-05-10 2006-03-08 ボルグワーナー・モールステック・ジャパン株式会社 油圧テンショナ
US5707309A (en) 1997-01-23 1998-01-13 Borg-Warner Automotive, Inc. Hydraulic tensioner with modular inlet check valve with pressure relief
US5967920A (en) * 1997-10-09 1999-10-19 Borg-Warner Automotive, Inc. Hydraulic tensioner with a bore cup
US5967921A (en) * 1997-10-09 1999-10-19 Borg-Warner Automotive, Inc. Hydraulic chain tensioner with molded plastic body
US5993341A (en) * 1997-11-25 1999-11-30 Borg-Warner Automotive, Inc. Hydraulic tensioner with a position actuated check valve assembly
US5911641A (en) * 1997-12-23 1999-06-15 Eaton Corporation Chain Tensioner and improved plunger retention thereof
DE69817344T2 (de) 1998-09-09 2004-06-09 Morse Tec Europe S.R.L. Triebketten- oder Riemenspanneinrichtung mit einem Kolben mit mehreren relativ zu einander bewegbaren Teilen
US6139454A (en) * 1998-09-21 2000-10-31 Borgwarner Inc. Hydraulic tensioner with plastic cap check valve or vent
US6117033A (en) * 1998-09-21 2000-09-12 Borgwarner Inc. Hydraulic tensioner with tuned spring piston
US6305763B1 (en) 1999-12-16 2001-10-23 Caterpillar Inc. Apparatus and method for operating a hydraulic excavator which has a position sensor for sensing position of an idler wheel
US6280010B1 (en) 1999-12-16 2001-08-28 Caterpillar Inc. Track tensioning assembly for adjusting tension on a drive track chain of a work machine having an actuator which includes a pair of concentrically arranged pistons
US6354678B1 (en) 1999-12-16 2002-03-12 Caterpillar Inc. Apparatus and method for adjusting tension of a drive track chain of a work machine which utilizes a sensor for sensing position of an undercarriage component
US6276768B1 (en) 1999-12-16 2001-08-21 Caterpillar Inc. Track tensioning assembly for adjusting tension on a drive track chain of a work machine having a slack adjuster device associated therewith
US6249994B1 (en) 1999-12-16 2001-06-26 Caterpillar Inc. Apparatus and method for operating track tensioning assembly of a hydraulic excavator
US6305762B1 (en) 1999-12-16 2001-10-23 Caterpillar Inc. Valve assembly for controlling actuation of an actuator of a track tensioning system
JP3687956B2 (ja) * 2001-01-25 2005-08-24 株式会社椿本チエイン 圧力油室を有するラチェット式テンショナ
US7070528B2 (en) * 2002-03-28 2006-07-04 Honda Giken Kogyo Kabushiki Kaisha Hydraulic tensioner lifter
DE102004043733A1 (de) * 2004-09-10 2006-03-16 Ina-Schaeffler Kg Gehäuse eines Spannsystems mit integrierter Spritzdüse
US7677718B2 (en) * 2004-12-17 2010-03-16 Hewlett-Packard Development Company, L.P. Flexible member having tensioning members
DE102005039740A1 (de) * 2005-08-23 2007-03-01 Schaeffler Kg Spannsystem
JP5102238B2 (ja) * 2008-04-02 2012-12-19 Ｎｔｎ株式会社 チェーンテンショナ
EP3670419B1 (de) * 2018-12-19 2023-01-25 Otis Elevator Company Verfahren und vorrichtung zur überwachung der kettenspannung

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DE1650910A1 (de) * 1967-09-01 1970-11-05 Winkelhofer & Soehne Joh Kettenspanner
DE2008472A1 (de) * 1970-02-24 1971-09-09 Daimler Benz Ag Hydraulischer Kettenspanner
DE2144688B2 (de) * 1971-09-07 1977-12-22 Klöckner-Humboldt-Deutz AG, 5000 Köln Keilriemen-spannvorrichtung
DE2819608A1 (de) * 1978-05-05 1979-11-08 Kloeckner Humboldt Deutz Ag Keilriemen-spannvorrichtung

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0472505B1 (de) * 1990-08-20 1995-09-27 TECNIDEA CIDUE S.r.l. Spannvorrichtung
EP0621419A1 (de) * 1993-04-20 1994-10-26 JOH. WINKLHOFER & SÖHNE GmbH & Co KG Kettenspanner mit Federvorspannung und hydraulischer Dämpfung
EP0686787A1 (de) * 1994-06-06 1995-12-13 JOH. WINKLHOFER & SÖHNE GmbH & Co KG Hydraulische Spanneinrichtung für endlose, flexible Getriebeelemente
US5637047A (en) * 1994-06-06 1997-06-10 Joh. Winklhofer & Soehne Gmbh & Co. Kg Hydraulic tensioner
GB2345112A (en) * 1998-12-22 2000-06-28 Sachs Automotive France Sa Hydraulic chain tensioner having a gas-purging orifice
GB2345112B (en) * 1998-12-22 2000-12-20 Sachs Automotive France Sa Hydraulic chain tensioner having a gas-purging orifice
EP1498580A2 (de) * 2003-07-16 2005-01-19 Renold Plc Ketten- oder Riemenspanner
EP1498580A3 (de) * 2003-07-16 2006-05-31 Renold Plc Ketten- oder Riemenspanner
US7331891B2 (en) 2003-07-16 2008-02-19 Renold Plc Tensioner for a chain or belt
US7634949B2 (en) 2005-07-23 2009-12-22 Renold Plc Transmission chain monitoring system
US7886613B2 (en) 2005-07-23 2011-02-15 Renold Plc Transmission chain monitoring system

Also Published As

Publication number Publication date
EP0348861A3 (en) 1990-06-13
JPH0257750A (ja) 1990-02-27
DE68910396T2 (de) 1994-03-03
DE68910396D1 (de) 1993-12-09
EP0348861B1 (de) 1993-11-03
US4826470A (en) 1989-05-02

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